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United States Patent |
5,711,532
|
Clark
,   et al.
|
January 27, 1998
|
Securing and centering devices for a split mechanical seal
Abstract
A split mechanical seal, for mounting to a stationary housing that contains
a rotating shaft, including first and second seal ring assemblies, at
least one resilient biasing element and at least one axial biasing
element. The first and second seal ring assemblies each include a seal
ring having two segments that are resiliently supported in the seal. The
segments have an outer surface and a pair of segment sealing faces
disposed at opposite ends of the segments. The resilient biasing element
is concentrically disposed about and in intimate contact with the outer
surface of one of the seal rings, for applying a first radially inward
force that biases the sealing faces of the seal ring segments into sealing
contact with each other. The mechanical seal includes a pair of resilient
biasing elements disposed about each seal ring, and the resilient biasing
element is preferably an elastomeric member. The axial biasing element is
associated with at least one seal ring for generating and applying, in
cooperation with the elastomeric member, a second radially inward force;
the second force operating to bias the segment sealing faces together when
the mechanical seal is exposed to a selected pressure condition. The axial
biasing element is an abutment, integrally formed with the segments of
both seal rings, that has a radially outwardly slanted outer surface. The
abutment transforms the axial force into an axial force component and a
second radially inward force component. This second radially inward
component also operates to bias the sealing faces of the seal ring
segments into sealing contact with each other. The seal further includes
integrally formed screw housings that have formed therethrough a
fastener-receiving aperture. The aperture has a tapped smaller-diameter
portion and an untapped larger diameter portion. The aperture mounts a
screw that has a screw-head and a shaft. The shaft has a tapped
larger-diameter distal end and a smaller-diameter proximal end. The screw
when mounted within the aperture, is positively maintained therein.
Inventors:
|
Clark; Marlen S. (Newburyport, MA);
Azibert; Henri V. (Windham, NH)
|
Assignee:
|
A. W. Chesterton Company (Stoneham, MA)
|
Appl. No.:
|
168874 |
Filed:
|
December 16, 1993 |
Current U.S. Class: |
277/320; 277/399 |
Intern'l Class: |
F16J 015/40 |
Field of Search: |
411/999,352
277/38,81 S,192
|
References Cited
U.S. Patent Documents
808082 | Dec., 1905 | Fuller.
| |
1177810 | Apr., 1916 | Rogness | 411/999.
|
1294620 | Feb., 1919 | Clarke.
| |
1467256 | Sep., 1923 | Thomson.
| |
1544609 | Jul., 1925 | Somes.
| |
2208859 | Jul., 1940 | Scott | 411/999.
|
2503086 | Apr., 1950 | Albright | 286/11.
|
2871040 | Jan., 1959 | Payne | 286/11.
|
2995391 | Aug., 1961 | Snyder | 286/11.
|
3006667 | Oct., 1961 | Stephens | 286/11.
|
3014742 | Dec., 1961 | Mayer | 286/11.
|
3025070 | Mar., 1962 | Copes | 277/39.
|
3031199 | Apr., 1962 | Laser et al. | 277/86.
|
3066942 | Dec., 1962 | Schwing | 277/62.
|
3101200 | Aug., 1963 | Tracy | 277/93.
|
3339952 | Sep., 1967 | Beckman | 411/999.
|
3421769 | Jan., 1969 | Boop et al. | 277/58.
|
3536333 | Oct., 1970 | Gits et al. | 277/37.
|
3556570 | Jan., 1971 | Cosenza | 411/999.
|
3599990 | Aug., 1971 | Grenier et al. | 277/4.
|
3836157 | Sep., 1974 | Hummer | 277/62.
|
3837658 | Sep., 1974 | Skinner et al. | 277/26.
|
3941394 | Mar., 1976 | Lukes | 277/40.
|
4088329 | May., 1978 | Junker | 277/26.
|
4377290 | Mar., 1983 | Netzel | 277/38.
|
4410188 | Oct., 1983 | Copes | 277/65.
|
4576384 | Mar., 1986 | Azibert | 277/81.
|
5059075 | Oct., 1991 | Kelly | 411/999.
|
5290132 | Mar., 1994 | Gnage et al. | 411/999.
|
Foreign Patent Documents |
605360 | May., 1926 | FR.
| |
1675200 | Dec., 1970 | DE.
| |
81152 | Aug., 1934 | SE.
| |
917693 | Feb., 1963 | GB.
| |
Primary Examiner: DePumpo; Daniel G.
Attorney, Agent or Firm: Lahive & Cockfield, LLP, Laurentano; Anthony A.
Claims
Having described the invention, what is claimed as new and desired to be
secured by Letters Patent is:
1. A split mechanical seal for mounting to a housing containing a rotating
shaft, said mechanical seal comprising
at least two arcuate gland segments, each said segment having an inner
surface and a pair of axially extending sealing faces, and having means
forming a fastener-receiving aperture for receiving a fastener, said
aperture formed substantially through each said seal face of said gland
segment at circumferentially aligned locations, and
each said aperture having a tapped portion axially spaced from said segment
sealing face and having a first diameter, and a clearance portion opening
onto said segment sealing face having a second diameter, said diameter of
said clearance portion being larger than said diameter of said tapped
portion, such that when said gland segments are assembled the
corresponding ones of said fastener-receiving apertures formed on each
seal face of each said gland segment are disposed opposite each other such
that said clearance portions open onto each other.
2. The seal of claim 1 further comprising securing means windingly mounted
within said fastener receiving aperture for securing said gland segments
together.
3. The seal of claim 2 wherein said securing means comprises at least one
fastener element, said fastener element includes a main shaft and a head
portion coupled to said shaft, said shaft having a threaded distal portion
having a first diameter and an untapped proximal portion having a second
diameter, said diameter of said threaded portion being greater than said
diameter of said proximal portion.
4. The seal of claim 3 wherein said diameter of said fastener distal
portion is close to said diameter of said aperture tapped portion, such
that when said fastener is windingly mounted within said aperture, said
fastener is positively maintained therein, thereby preventing loss of said
fastener.
5. The seal of claim 1 wherein each said gland segments have integrally
formed thereon one or more integrally formed screw housings being
apertured with said fastener-receiving aperture means.
6. The seal of claim 5 further comprising securing means windingly mounted
within said fastener receiving aperture for securing said gland segments
together.
7. The seal of claim 6 wherein said securing means comprises at least one
fastener element, said fastener element includes a main shaft and a head
portion coupled to said shaft, said shaft having a threaded distal portion
having a first diameter and an untapped proximal portion having a second
diameter, said diameter of said threaded portion being greater than said
diameter of said proximal portion.
8. The seal of claim 7 wherein said diameter of said fastener distal
portion is close to said diameter of said aperture tapped portion, such
that when said fastener is windingly mounted within said aperture, said
fastener is positively maintained therein, thereby preventing loss of said
fastener.
9. The seal of claim 1, wherein said fastener-receiving apertures are
adapted to be disposed in registration with each other when assembled such
that same ones of said apertures are disposed along a common axis to form
a continuous fastener passage having in succession along said axis a first
tapped passage portion disposed at one end, a pair of intermediate
adjacent clearance passage portions, and a second tapped passage portion
disposed at an opposite end, said axial succession of passage portions
allowing mounting of a fastener element from either end of said common
passage.
Description
BACKGROUND
This invention relates generally to mechanical seals. More particularly,
the present invention relates to universal split mechanical seals that
provide strong sealing capabilities under different operating conditions.
Split mechanical seals with resiliently mounted faces are employed in a
wide variety of mechanical apparatuses to provide a pressure-tight and
fluid-tight seal. The mechanical seal is usually positioned about a
rotating shaft that is mounted in and protruding from a stationary
housing. The seal is usually bolted to the housing at the shaft exit, thus
preventing the loss of pressurized process fluid from the housing.
Conventional split mechanical seals include face type mechanical seals,
which include a pair of sealing rings that are concentrically disposed
about the shaft, and axially spaced from each other. The sealing rings
each have sealing faces that are biased into sealing contact with each
other. Usually, one seal ring remains stationary, while the other ring
contacts the shaft and rotates therewith. The mechanical seal prevents
leakage of the pressurized process fluid to the external environment by
biasing the seal ring sealing faces in sealing contact with each other.
The rotary seal ring is usually mounted in a holder assembly which is
disposed in a chamber formed by a gland assembly. The holder assembly has
a pair of holder halves, each having a pair of sealing faces, that are
secured together by a number of screws. Likewise, the gland assembly has a
pair of gland halves, each having a pair of sealing faces, that are also
secured together by a number of screws. The sealing rings are often
divided into segments, each segment having a pair of sealing faces,
thereby resulting in each ring being a split ring that can be mounted
about the shaft without the necessity of freeing one end of the shaft
ends.
Each holder and gland half has formed on one of the sealing faces a gasket
groove for mounting a sealing gasket. When the gasket is mounted within
the groove and the halves are secured together by the screws, the gasket
is placed in intimate facing contact with the opposite sealing face of the
holder or gland half. This facing contact forms a pressure-tight and a
fluid-tight seal between the respective gland and holder halves.
The gland assembly is usually centered on the stationary housing prior to
securing thereto by centering the shaft and holder assembly disposed
within the chamber formed by the gland assembly, thereby determining the
proper mounting position of the gland assembly. Conventional methods for
centering the gland assembly include using a number of plastic elongated
tabs mounted on the exterior seal housing at an outboard end of the seal.
The plastic tabs protrude evenly into the gland chamber, centering the
shaft and holder assembly.
Another drawback of conventional split seals is that the screws which
secure the gland and holder segments together are usually mounted in
predetermined tapholes, which typically necessitate rotating the shaft
after securing one screw, to affix the other screws. Additionally, during
disassembly of the mechanical seal, the screws can become disengaged from
either segment of the gland and holder, thereby increasing the likelihood
that the screws can become detached and damage other components of the
housing, or lost.
Still another drawback of the conventional seals is that the conventional
centering mechanisms center off the shaft at the outboard end of the seal.
In applications where there is a minimal distance between the seal
outboard end and an axial obstruction it is difficult to insert the
centering mechanism. Consequently, it is difficult to center the gland
assembly relative to the shaft. Additionally, the plastic tabs can become
disengaged from the seal, increasing the likelihood that the tabs can
become lost. Further conventional seals employing integrally formed
centering mechanisms add distance to the overall length of the seal, which
can preclude the use of the seal.
As the above described and other prior art sealing systems have proven less
than optimal, an object of this invention is to provide an improved
mechanical seal that provides a fluid-tight seal under a variety of
operating pressure conditions.
Another object of the invention is to provide a single split mechanical
seal that can function under different operating pressures, thereby
eliminating the need for employing different seals.
Still another object of the invention is to provide a split mechanical seal
that is relatively easy to assemble and to disassemble.
Yet another object of the invention is to provide a seal centering
mechanism that is relatively easy to manipulate, while being able to
function in different seal assemblies.
Other general and more specific objects of this invention will in part be
obvious and will in part be evident from the drawings and the description
which follow.
SUMMARY OF THE INVENTION
These and other objects are attained by the invention which provides, in
one aspect, a split mechanical seal for mounting to a stationary housing
that contains a rotating shaft. The mechanical seal includes first and
second seal ring assemblies, at least one resilient biasing element and at
least one axial biasing element. The first and second seal ring assemblies
each include a seal ring having two segments that are resiliently
supported in the seal. The segments have an outer surface and a pair of
segment sealing faces disposed at opposite ends of the segments. The first
seal ring is a stationary seal ring and the second seal ring is a rotary
seal ring.
In one aspect of the invention, the resilient biasing element is
concentrically disposed about and in intimate contact with the outer
surface of one of the seal rings, for applying a first radially inward
force that biases the sealing faces of the seal ring segments into sealing
contact with each other. In a preferred embodiment, the mechanical seal
includes a pair of resilient biasing elements disposed about each seal
ring, and the resilient biasing element is preferably an elastomeric
member.
In another aspect of the invention, the axial biasing element is associated
with at least one seal ring for generating and applying, in cooperation
with the elastomeric member, a second radially inward force. The second
force also operates to bias the segment sealing faces together when the
mechanical seal is exposed to a selected pressure condition. In a
preferred embodiment, the axial biasing element is an abutment, integrally
formed with the segments of both seal rings, that has a radially outwardly
slanted outer surface.
According to another aspect of the invention, when the mechanical seal is
exposed to the selected pressure condition, e.g., ambient pressure greater
than the internal pressure of the mechanical seal, the elastomeric member
is disposed in intimate contact with the abutment, and applies an axial
force thereto. The abutment transforms the axial force into an axial
component and a second radially inward component. This second radially
inward component also operates to bias the sealing faces of the seal ring
segments into sealing contact with each other.
According to a preferred practice of the invention, the split seal ring of
this invention includes one ring mounted in a holder assembly to rotate
with the rotating shaft, and a second ring mounted in a gland assembly
fixed to the stationary housing surrounding the shaft. Each of the seal
rings has a sealing face brought into sealing contact with the other to
form a seal while the faces are rotating with respect to one another. In
order to provide for convenient assembly and disassembly of the seal about
the shaft, the seal rings, as well as the housing assembly and the gland
assembly, are formed in segments. It is a significant feature of the
present invention that each of the seal ring segments be allowed to move
axially with respect to one another, while maintaining the individual
rings biased toward one another into sealing contact. This is accomplished
by resiliently mounting each ring in its respective holder and gland while
providing axial bias toward the interface therebetween.
In this configuration it is also essential that the seal ring segments be
resiliently biased in the radial direction to maintain the sealing contact
at the segment interfaces where the segments join to form the individual
rings. In a typical embodiment, this is accomplished by placing a circular
elastomer O-ring around the periphery of each seal ring. Since the purpose
of the overall seal assembly is to maintain a seal between ambient
atmosphere and the internal fluids surrounding the rotating shaft, these
segment seals must be capable of maintaining their sealed condition for a
variety of pressure conditions between the ambient atmosphere and the
internal fluids. These may include a higher pressure in the ambient as
compared to the internal fluid or vice versa. The elastomer O-rings also
provide for resilient mounting of the rings with respect to axial
movement, and some axial biasing of the rings toward one another. The
fluid spaces within the mechanical seal are such that when the internal
fluid pressure is negative with respect to the ambient it creates a radial
biasing force which tends to open the intersegment seals, thereby leaking
ambient fluid into the process fluid. This occurs despite the fact that
fluid pressure exerts an axial force against the O rings moving them
toward increased contact at the interface between the rotating seal ring
and the stationary seal ring.
In the present inventive mechanical seal, this problem is addressed by
providing a seat for the O-ring about the seal ring segments that has a
sloping outer surface such that axial pressure by the O-ring against that
surface is converted into both axial and radial components so that the
radial component, directed toward the center of the ring, maintains the
above intersegment seals.
According to a further aspect of the invention, the gland segments and the
holder segments include seal faces having formed thereon a gland gasket
groove and a holder gasket groove, respectively. The gland groove mounts a
gland gasket, and when disposed therein, has an exposed portion that
extends beyond the gland seal face. The exposed gasket portion is captured
in, rather than sealingly abuts, the gland groove formed on the seal face
of the other gland segment. Likewise, the holder groove mounts a holder
gasket that has an exposed portion extending from the holder seal face
that is captured in the holder groove formed on the sealing face of the
other holder segment.
According to another aspect of the invention, the gland and holder assembly
are apertured with one or more fastener-receiving apertures. The aperture
has a tapped portion axially spaced from the segment sealing face and a
clearance portion, opening onto the sealing face, that has a diameter
larger than the tapped portion. The aperture mounts a fastener, such as a
screw, that has a shaft and a screw-head. The shaft includes a threaded
distal portion and a proximal portion, where the diameter of the distal
portion is greater than the diameter of the proximal portion. This
configuration positively maintains the screw the within the aperture,
preventing loss of the screw.
According to other aspects of the invention, the gland and holder
assemblies have integrally formed therein a pair of screw housings. The
housings have an aperture formed therethrough that is adapted to receive a
centering strap. The centering strap circumferentially and uniformly
separates the gland assembly from the holder assembly disposed about the
shaft.
In another preferred practice of the invention, the holder segments have an
outer surface that have mounted thereon a number of wearable protrusions.
The protrusions uniformly separate the holder segment outer surfaces from
an inner surface of the gland assembly.
The foregoing and other objects, features and advantages of the invention
will be apparent from the following description and apparent from the
accompanying drawings, in which like reference characters refer to the
same parts throughout the different views. The drawings illustrate
principles of the invention and, although not to scale, show relative
dimensions.
BRIEF DESCRIPTION OF THE DRAWINGS
FIG. 1 is a perspective view of a split mechanical seal separated into two
segments according to a preferred embodiment of the invention;
FIG. 2 is a fragmentary view of the mechanical seal of FIG. 1;
FIG. 3 is an exploded unassembled view of one half of the mechanical seal
of FIG. 1 taken along line 3--3;
FIG. 4 is an a perspective view of one-half of the mechanical seal of FIG.
1;
FIG. 5 is a top fragmentary view of a portion of the mechanical seal of
FIG. 1;
FIG. 6A is a side view of a gland or holder screw according to a preferred
embodiment of the invention;
FIG. 6B is a broken perspective view of the screw housing of FIG. 1
according to a preferred embodiment of the invention.
FIG. 7 is a sectional view of an elastomeric member;
FIG. 8A is a fragmentary view of a stationary seal ring and gland assembly
of FIG. 1 according to a preferred practice of the invention;
FIG. 8B shows the movement of the O-ring of FIG. 8A according to a
preferred practice of the invention;
FIG. 9 is a view similar to FIGS. 8A and 8B showing an alternate
embodiment;
FIG. 10 is a plan view of a holder assembly according to a preferred
embodiment of the invention; and
FIG. 11 is a plan view of the mechanical seal of FIG. 1 showing a centering
mechanism according to one preferred embodiment.
DESCRIPTION OF ILLUSTRATED EMBODIMENTS
FIGS. 1-4 depict a split mechanical seal 10 according to a preferred
embodiment of the invention. The mechanical seal 10 is preferably
concentrically disposed about a shaft 12 that extends along a first axis
13 and is secured to an external wall of a housing 14, such as a pump or
the like. The shaft is mounted, at least partly, within the housing. The
mechanical seal 10 constructed in accordance with the teachings of this
invention provides a fluid-tight seal, thereby preventing a process
medium, e.g., hydraulic fluid, from escaping the housing 14. The
fluid-tight seal is achieved by a pair of split seal rings 20 and 30, a
first or rotating seal ring 20 and a second or stationary seal ring 30,
each having a smooth arcuate sealing surface 21, 31 and a pair of segment
sealing faces 22, 32. The smooth arcuate sealing surface of each seal ring
is biased into sealing contact with the corresponding surface of the other
seal ring segment. Similarly, the segment sealing faces 22,32 of the ring
segments 25 and 33 are biased into sealed relationship with each other.
Thus, these individual seal faces provide a fluid-tight seal operable
under a wide range of operating conditions, including a vacuum condition,
as described in greater detail below.
The illustrated mechanical seal 10 includes, in addition to the rotary seal
ring 20 and the stationary seal ring 30, a seal gland assembly 40 and a
seal ring holder assembly 110. The seal gland assembly 40 has a pair of
gland segments 41, 42, each segment identical to the other. The gland
segment 41 has an inner surface that has a first face 46, and an
integrally formed and radially stepped outwardly second face 50. The first
face 46 and the second face 50 form, in combination, a first connecting
annular wall 48. A stepped third face 54 extends radially outward from the
second face 50 and forms, in combination therewith, a second annular
connecting wall 52. A sloped fourth face 56 extends radially inward from
the gland segment third face 54.
The gland assembly 40 has a housing gasket groove 58 formed along a bottom
59 of the gland assembly 40. The groove 58 seats a flat, annular
elastomeric gasket 60. As illustrated in FIGS. 2 and 3, the gasket 60
preferably has an axial dimension greater than the depth of the groove 58,
thereby providing a pressure-tight and fluid-tight seal between the
mechanical seal 10 and the housing 14. In a preferred embodiment, the
housing gasket 60 is pre-cut into two arcuate segments for mounting in
each gland segment 41, 42. The housing gasket segments are preferably
mounted in the groove 58 and secured thereto by an adhesive. This
arrangement helps prevent leakage of the process medium along the seal 10
when mounted to the housing 14.
Each gland seal face 64, 66 has formed thereon a gland gasket groove 70.
The groove 70 has a main axial portion 71 which extends from the gland
second face 50 to the gland fourth face 56. Groove segments 72, 73,
transverse to the main groove segment 71, extend along the second gland
wall 52 and the gland fourth face 56, respectively, and groove segment 74,
spaced radially inward from groove segment 71, extends along the gland
segment second face 50.
An elastomeric gland gasket 76, complementary in shape to the gland groove
70, seats in the groove 70. It is a significant feature of the present
invention that the gasket 76, when seated in the groove 70, extends beyond
the gland split faces 64, 66, as best shown in FIGS. 1, 4 and 5. The
exposed portion of the gasket 76 is captured in a complementary groove
formed on the split gland seal face of the other gland segment 42.
Capturing both ends of the gasket 76 between opposing split gland seal
faces prevents the gasket 76 from extruding into the gap formed between
the split gland seal faces when subjected to pressures higher than a
selected maximum pressure. This double-capturing feature thus allows the
gland segments 41, 42 to withstand greater pressures without developing
pressure leaks, as well as relaxing the mechanical tolerances of other
components of the mechanical seal 10. The gland gasket 76 is preferably
formed from any suitable resilient material, such as elastomeric rubber.
Further, although the gasket 76 has the illustrated shape, those of
ordinary skill will recognize that the gasket 76 and its corresponding
groove 70 can have any suitable geometric configuration.
Each of the gland segments 41, 42 also have integrally formed therewith a
pair of screw housings 80, 82. Each screw housing has a transverse
fastener-receiving aperture 84 formed substantially therethrough. The
aperture 84 has a tapped smaller-diameter portion 86, and a concentric
untapped larger-diameter portion 88, as shown in FIGS. 1, 6A and 6B.
Preferably, the untapped portion 88 of the aperture 84 is disposed closest
to the gland seal faces 64, 66. Furthermore, the apertures 84 are formed
at circumferentially aligned positions on each gland segment 41, 42, e.g.,
on each axial seal face.
The transverse aperture 84 mounts a screw 90 having the illustrated
configuration. The screw 90 preferably has a main shaft 92 and a
screw-head portion 96. The screw shaft 92 has a threaded distal portion 93
and an untapped proximal portion 94, as shown in FIGS. 1 and 6A. The outer
diameter of the threaded portion 93 is greater than the outer diameter of
the proximal portion 94. As illustrated in FIG. 6B, each screw 90 fastens
together a pair of housings 80 and 82. When the threaded distal portion 93
of the screw 90 is screwed into the tapped portion 86 of the aperture 84,
the distal portion 93 is positively maintained in the aperture 84. As the
screw 90 further travels through the aperture 84, the screw distal end
enters the untapped portion 88, or clearance gap of the aperture 84. In
this orientation, the screw 90, although not snugly secured, is still
positively maintained (i.e., not detachable) in the aperture 84. In a
preferred embodiment, the diameter of the screw distal portion 93 is close
to the diameter of the tapped smaller-diameter portion 86 of the screw
housings 80,82.
Significant advantages are enjoyed by the screw 90 and the aperture 84 of
the present invention. In particular, the screw 90 can be mounted in the
fastener-receiving aperture 84 from any side of either gland segment 41,
42 prior to assembly, which is particularly useful in limited access
installations, and is positively maintained in the screw housing 80. By
preventing the screw 90 from completely detaching from the screw housing
80 prevents accidental loss of the screw 90 during assembly and
disassembly, thus facilitating assembly of the seal while reducing
installation time. The same construction pertains to the screw housings
82.
The gland assembly 40 further includes a plurality of bolt-tabs 38. The
bolt-tabs 38 have a main body 37 that has integrally formed at one end an
inserting-tab projection 39. The tab projection 39 mounts in an annular
groove 68 formed around the periphery of the gland assembly 40. The
angular position of the tabs can be adjusted by sliding the bolt-tab 38
and the tab projection 39 about the groove 68. The bolt-tabs 38 help
secure the mechanical seal 10 to the housing 14 by seating mounting bolts
(not shown). In use, the mounting bolt is inserted between a pair of
adjacent bolt-tabs. The bolt-tabs 38 are further described in detail in
U.S. Pat. No. 5,209,496, assigned to the assignee hereof and which is
herein incorporated by reference.
As illustrated in FIGS. 1.varies.4, a holder assembly 110 is disposed in a
chamber 24 formed by the gland assembly 40, and spaced radially inward
therefrom. It should be understood however, that the holder assembly 110
need not be disposed within the gland assembly. Rather, the holder can be
axially spaced from the gland assembly 40. The holder assembly 110 has a
pair of arcuate holder segments 112, 114, each identical to the other.
Each holder segment 112, 114 has an outer surface 116 and an inner surface
124. The holder segment inner surface 124 has a radially inward sloping
first face 126 that terminates in an axially extending second face 130. A
pair of successive radially inward stepped surfaces form a third face 134
and a fourth face 138, respectively. The second face 130 and the third
face 134 have a radially inward extending first wall 132 integrally formed
therebetween, and the third face 134 and the fourth face 138 have a
radially inward extending second wall 136 integrally formed therebetween.
The diameter of the fourth face 138 is preferably equal to or slightly
greater than the diameter of the shaft 12, to which the holder assembly
110 is to be attached.
The holder segment outer surface 116 has a first axially extending outer
surface 146, a radially inward sloping second outer surface 148, and a
radially inward stepped third outer surface 154. The third outer surface
154 and the second outer surface 148 form, in combination, a radially
inward extending first outer wall 150. In a preferred embodiment, the
outer diameter of the holder segment third outer surface 154 is less than
the diameter of the gland segment fourth face 56. This clearance is
necessary to allow the holder assembly 110 to seat within the gland
assembly 40 for unobstructed rotational movement therein. The outer
diameter of the first outer surface 146 is preferably less than the inner
diameter of the gland segment third face 54, and preferably greater than
the gland segment second face 50.
The fourth face 138 of the holder segment 112 has formed thereon an annular
channel 140 for mounting a split shaft gasket 142. When mounted in the
channel 140, the gasket 142 sealingly mates with the shaft 12, providing a
fluid-tight seal along the holder and shaft interface (see FIG. 2). The
second wall 136 preferably has axially extending therefrom a cylindrical
protrusion 144. The protrusion 144 operates as a mechanical rotary means
by biasing the rotary seal ring 20 into rotational movement, as described
in greater detail below.
The holder segments 112, 114 have formed on each split holder seal face 118
and 120 a holder gasket groove 158, having the configuration illustrated
in FIGS. 1-4. A holder gasket 160, complementary in shape to the groove
158, seats in groove 158. It is also a significant feature of the present
invention that the holder gasket 160, when seated in the groove 158,
extends beyond the holder seal faces 118, 120, as best shown in FIG. 4.
The exposed portion of the gasket 160 seats in a complementary groove
formed in the opposite holder segment seal face. This arrangement provides
for a fluid-tight seal at pressures higher than a selected value, as
described above. The gasket is preferably composed of any suitable
deformable material, such as elastomeric rubber.
The holder segments 112, 114 also have a fastener-receiving aperture 164
that mounts screw 170. The holder aperture 164 is similar to the
fastener-receiving aperture 84 of the gland screw housing 80,82, and the
screw 170 is similar to the screw 90. Likewise, the screw 170 and aperture
164 operate in the aforementioned manner.
The holder assembly 110, the gland assembly 40, and the screws 90 can be
formed from any suitably rigid material, such as stainless steel.
The rotary seal ring assembly 20 also includes a pair of arcuate rotary
seal ring segments 25. The rotary ring segments have a substantially
smooth arcuate inner surface 172 and an outer surface 176, as best shown
in FIG. 3. The inner surface 172 has formed thereon a generally
rectangular notch 174. The notch 174 mounts over the holder protrusion
144. The rotary segment outer surface 176 has an axially extending first
outer surface 180 that terminates in a radially inward sloping second
outer surface 182 or abutment, and an axially extending third outer
surface 184. The rotary segment 25 also has the smooth arcuate sealing
surface 21 disposed at the top of the ring 20. The inner diameter of the
rotary seal segments inner surface 172 is greater than the diameter of the
shaft to permit mounting thereon. The diameter of the rotary seal segment
third outer surface 184 is equal to or slightly less than the diameter of
the holder segment third face 134, for mounting engagement with the holder
assembly 110. The diameter of the rotary seal segment first outer surface
180 is less than the inner diameter of the holder segment first face 126,
and greater than the diameter of the holder third face 134.
Although the illustrated seal ring 20 has an abutment 182 formed at the
outer surface 176, those of ordinary skill will recognize that a
non-sloping stepped annular surface could also be employed.
An elastomeric member, such as O-ring 188, is concentrically disposed about
the rotary seal ring 20. In a preferred embodiment, the O-ring 188 seats
along the first wall 132 of the holder assembly 110 and abuts the second
and third outer surfaces 182, 184 of the rotary seal ring 20, as shown in
FIG. 2. The O-ring 188 is sufficiently resilient to place each of the
rotary segment sealing faces in sealing contact with another segment,
thereby forming a fluid-tight and pressure-tight seal. The O-ring 188 also
functions, in cooperation with a mechanical clip 200, as an axial
resilient biasing means by floatingly and non-rigidly supporting the
rotary and stationary seal rings 20,30 in axially spaced floating relation
relative to the rigid walls and faces of the gland and holder assemblies
40, 110. This floating relationship was first described in U.S. Pat. No.
4,576,384, assigned to the assignee hereof, and is herein incorporated by
reference.
As best shown in FIG. 3, the stationary seal ring 30 similarly includes a
pair of arcuate seal ring segments 33, 33, each identical to the other.
The stationary seal ring arcuate segments 33 have a substantially smooth
arcuate inner surface 35 extending parallel to the first axis 13 and an
outer surface 36. The stationary seal ring segment outer surface 36 has an
axially extending first outer surface 190 that terminates in a radially
outward extending abutment 192. The stationary seal ring 30 has a
substantially smooth arcuate top surface 194 and a smooth arcuate ring
sealing surface 31 disposed at the bottom of the ring. The stationary seal
segment 33 has a recess 196 formed along the top surface 194. A mechanical
clip 200, mechanically coupled to a top surface 62 of the gland assembly
40 via clip groove 63, seats in the recess 196. This arrangement helps
align and seat the stationary seal ring 30 in the chamber 24, as well as
functioning as a mechanical impedance for preventing the stationary seal
ring 30 from rotating with the shaft 12 and the rotary seal ring 20.
The inside diameter of the stationary segment inner surface 35 is greater
than the shaft diameter, and is greater than the diameter of the inner
surface 172 of the rotary seal ring 20, thereby allowing relative motion
therebetween. An elastomeric member, e.g., O-ring 202, provides a radially
inward biasing force sufficient to place the segment sealing faces 32 of
stationary seal ring segment 33 in sealing contact with the other
stationary seal ring segment. Additionally, O-ring 202 forms a fluid-tight
and pressure-tight seal between the gland assembly 40 and the stationary
seal ring 30. The O-ring 202 seats in a first mounting region 204 defined
by the gland segment first wall 48, the gland second face 50, the
stationary ring out surface 190, and the stationary ring abutment 192. In
a preferred embodiment, the abutment 192 forms an angle relative to the
stationary ring outer surface 190 preferably in the range of about
30.degree. to about 60.degree., and most preferably about 45.degree.. The
stationary seal ring 30 is preferably composed of a carbon or ceramic
material, such as alumina or silicon carbide and the like.
The mechanical clip 200 also functions as an axial biasing means by
providing resilient support for the stationary and rotary seal rings 20,
30 by axially biasing the seal rings such that the stationary and rotary
sealing surfaces 21 and 31 are disposed in sealing contact with each
other. As illustrated in FIG. 2, the seal rings 20, 30 are floatingly and
non-rigidly supported in spaced floating relation relative to the rigid
walls and faces of the gland and holder assemblies 40, 110. This floating
and non-rigid support and spaced relationship permits small radial and
axial floating movements of the rotary seal segments 25,25 and the
stationary seal segments 33,33 with respect to the shaft 12, while still
allowing the rotary sealing surface 21 to follow and to be placed in
sealing contact with the smooth arcuate sealing surface 31 of the
stationary seal ring 30. Thus, the rotary and stationary seal ring sealing
surfaces 21 and 31 are self-aligning as a result of this floating action.
As generally illustrated in FIG. 7, identical ball and socket fastening
mechanisms are provided on the free ends of O-rings 188 and 202. At one
end, O-ring 202 narrows into a substantially hemispherical shoulder
portion 222 and, adjacent thereto, annular neck portion 224. immediately
adjacent neck portion 224 is substantially spherical head portion 226. In
fastening, head portion 224 is inserted into matching spherical socket
portion 227 at the other end of O-ring 202 such that annular collar
portion 228 surrounds and captures neck portion 224, and shoulder portion
222 is in intimate contact with annular jacket portion 230. Additionally,
although the mechanical seal 10 and its associated components are depicted
as sectional parts, the O-rings 188 and 202 are continuous and complete
structures having the above configuration.
In assembly, the rotary seal segments 25,25 are mounted about the shaft 12
and mounted in the holder assembly 110 by aligning the rectangular notch
174 of the rotary seal ring segment 25 with the axially extending holder
protrusion 144. The O-ring 188 is concentrically disposed about the rotary
seal segments 25, and is further placed in sealing contact with the holder
second face 130, the holder first wall 132, and with the rotary seal outer
surfaces 182, 184. The O-ring 188 provides an inward radial force
sufficient to place the rotary seal faces 22 of the seal segment 25 in
sealing contact with each of the sealing faces 22 of the other rotary
segment. The holder segments 112, 114 are then secured together by
tightening the screws 170 that are positively maintained in the
fastener-receiving apertures 164. As shown in FIGS. 1-3, the rotary seal
ring segments 25,25 are spaced from the holder assembly inner surfaces
124, and are non-rigidly supported therein by the O-ring 188, thereby
permitting small radial and axial floating movements of the rotary seal
ring 20.
The stationary seal ring segments 33 are concentrically mounted over the
shaft 12, and secured together by O-ring 202. The O-ring 202 applies a
radially inward force to the stationary seal ring outer surface 36
sufficient to place the segment sealing faces 32 of each segment in
sealing contact with each other.
The gland segments 41,42 are concentrically placed about the holder
assembly 110 and the rotary and stationary seal rings 20,30, and are
secured together by screws 90 that are mounted in and positively
maintained by the fastener-receiving apertures in the screw housings 80
and 82. The screws 90 cannot be unintentionally removed from the
mechanical seal 10 since they are secured to the gland assembly 40 by the
inventive fastener-receiving aperture 84 and screw 90. Additionally,
mounting the screws 90 does not necessitate rotating the shaft since the
screws 90 can be secured from the same or opposite sides of the gland
assembly 40.
Prior to fully securing the gland screws 90 to the housing 14, the shaft
12, the holder assembly 110, and the rotary and stationary seal rings
20,30 should be centered within the chamber 24. According to this
inventive mechanical seal, the shaft 12 and holder assembly 110 center the
gland segments 41,42 by way of centering spacers 240 formed along the
outer surface 116 of the holder assembly 110, as shown in FIG. 10. The
spacers can be integrally formed on the holder outer surface 116, or can
be mounted in depressions formed along the holder outer surface 116. In a
preferred embodiment, the spacers 240 are circumferentially and evenly
spaced about the first outer surface 146 of the holder assembly 110. The
spacers 240 are preferably formed of a soft wearable material, such as
teflon, which prevents scoring of the gland inner surface during
rotational movement of the holder assembly 110. Although the FIG. 10
embodiment shows four evenly separated spaces, any number and spacing of
spacers can be employed. Additionally, the spacers 240 need not be formed
on the holder first outer surface 146, but can be formed at various holder
locations.
An alternate embodiment of a shaft centering mechanism is depicted in FIG.
11. In FIG. 11, a centering strap 241 passes through a transverse port 242
formed in the screw housings 80 and 82. The centering strap 241 includes a
pair of flexible elongate segments 244,246 attached to a handle 248. The
transverse port 242 opens onto the exterior of the screw housing 80, (or
82) and into the chamber 24 formed by the gland assembly 40. The hexagonal
bolt (not shown) caps this opening and isolates the interior of the port
from the ambient environment. The strap is preferably made of a plastic
material. When centering the shaft 12 and the holder assembly 110 in the
chamber 24, the front ends 250,252 of the centering strap 241 are inserted
into the port 242 until the ends 250,252 contact the holder assembly 110,
temporarily impeding the path of the strap 241. As the strap 241 is
further inserted into the port 242, the strap ends 250,252 travel about
the periphery of the holder assembly 110, until the strap nearly encloses
the holder assembly 110. Thus, the strap functions to uniformly space the
holder assembly 110, and thus the shaft 12, from the gland inner surface.
Those of ordinary skill will recognize that the centering mechanisms can
be employed in both split and non-split mechanical seals.
When the gland assembly 40 and the holder assembly 110 are properly
aligned, the gland gasket 76 and the holder gasket 160 are captured in
separate gasket grooves formed on opposite sealing faces of the gland and
holder segments. This double-capture configuration allows the mechanical
seal 10 to withstand higher pressures without degradation of the pressure
and fluid seals formed at the segment sealing faces. Additionally, the
O-ring 202 forms a pressure-tight and fluid-tight seal between the gland
inner surface, e.g. gland second face 50 and first wall 48, and the outer
surface 36 of the stationary seal ring 30.
After the mechanical seal is assembled and mounted to the pump housing 14,
the pump process medium, e.g. hydraulic fluid, is sealed within a process
medium channel 234, as shown in FIG. 2, defined by the gland inner surface
54 (excluding the gland first face 46), O-ring 202, the holder assembly
outer surface 116, the stationary seal ring outer surface 190 and abutment
192, the rotary seal ring first and second surfaces 180, 182, the holder
assembly first and second faces 126, 130, and O-ring 188. The ambient
environment medium, typically air, fills an ambient process channel 236,
typically sealed from the process channel 234, that is defined by the
stationary and rotary seal ring inner surfaces 35,172, the stationary ring
outer surface 190, the gland first and second faces 46,50 and first wall
48, the rotary seal ring third outer surface 184, and the holder assembly
first wall 132. The phrase "ambient environment" is intended to include
any external environment other than the internal environment of the
housing 14.
The stationary and rotary seal ring segment sealing faces 22,32 are placed
in sealing contact with the other segment of the pair by the radial force
of the O-rings 188 and 202. In addition, the hydraulic pressure of the
process medium contained within the process channel 234 exerts an
additional radially inward force, proportional to the fluid pressure, upon
the seal ring segment outer surfaces 36, 190, biasing the segment sealing
faces 32 together.
Overall, the O-ring 142 prevents the seepage of process medium along the
shaft 12 and into the ambient process channel 236. The flat O-ring 60
prevents the seepage of process medium along the housing 14 and mechanical
seal 10 interface and the O-rings 188 and 202 prevent process medium from
invading the ambient process channel 236 by way of the holder assembly 110
and the gland 40, respectively.
In operation, when the pressure of the process medium is greater than or
equal to the pressure of the ambient environment medium (positive
pressure), the O-ring 202 is seated in position A in the first mounting
region 204, as shown in FIGS. 2, 4 and 8A. In this position, the process
medium exerts an inward radial force upon the stationary seal ring outer
surface 36, depicted in FIG. 8A as solid arrows, and applies an axial
force (to the right in FIG. 8A) upon O-ring 202, sealing the O-ring
against the first wall 48 of the gland inner surface and the stationary
seal ring outer surface 190.
When the pressure of the process medium falls below the pressure of the
external environment (negative pressure or vacuum), the ambient process
medium biases O-ring 202 into position B disposed against the abutment
192, as shown in FIG. 8B. The phrase "negative pressure" is intended to
include any pressure situation which results in the process medium being
at a lower pressure than the ambient medium. The pressure applied by the
ambient environment produces both an inward radial force and an outward
radial force upon the stationary seal ring segments 35, 36, as shown by
the solid arrows. In the first mounting region, the area that was formally
occupied by process fluid and which was evacuated by the movement of the
O-ring 202 (to the left in FIG. 8B) is now occupied by the ambient medium.
The radially inward and outward forces generated by the ambient medium
cancel along the length of the seal ring segment to the right of the
dashed line 260, thus producing no net force. However, to the left of the
dashed line 260 and of the O-ring 202, the outward radial force applied to
the inner surface 35 of the stationary seal ring 30 is greater than the
opposing pressure produced by the process medium, producing a net outward
radial force. Opposing this outward force is O-ring 202. However, when the
radially outward force exceeds the biasing force produced by the O-ring
202, the stationary seal segments separate along the sealing faces 32,
thereby breaking the fluid-tight seal and exposing the process channel 234
to the ambient medium.
However, when the ambient medium forces the O-ring against the abutment
192, generating an axial force, the sloped abutment surface transforms
this normal force into an axial force component 268 and a radial force
component 270. The radial force component 270 forms a second or
supplemental inward radial force. In a preferred embodiment, with the
abutment slope forming a 45.degree. angle, the second force component 270
is 0.707 times the magnitude of the outward radial force. For most
pressure situations, this second radial force is sufficient to prevent the
seal faces 32 of the stationary seal rings from separating, thus
maintaining the fluid-tight seal. Furthermore, the axial force component
268 operates to maintain the smooth arcuate sealing surfaces 21 and 31 of
the stationary and rotary seal rings 20,30 in sealing contact with each
other.
According to a preferred practice of the invention, the sealing surfaces 21
and 31 of the stationary and rotary seal rings 20,30 can further be
maintained in sealing contact with each other by reducing the net outward
radial force. One preferred practice is to minimize the area of the
stationary ring 30 exposed to the unbalanced outward radial force. As
shown in FIG. 8B, the portion of the seal ring 30 to the left of the
dashed line 260 is preferably minimized, thereby reducing the outward
radial force applied to the seal ring inner surface 35 by the higher
pressure ambient medium.
In an alternate embodiment, as shown in FIG. 9, an intermediate force
element 280 can be disposed between the stationary seal ring 30 and the
gland inner surface. In a manner similar to that explained above, O-ring
202A, in cooperation with abutment 192, generate the second radial inward
force, thereby maintaining the fluid-tight seal. Meanwhile, O-ring 202B
creates a fluid seal between the process medium channel 234 and the
ambient channel 236.
It will thus be seen that the invention efficiently attains the objects set
forth above, among those made apparent from the preceding description.
Since certain changes may be made in the above constructions without
departing from the scope of the invention, it is intended that all matter
contained in the above description or shown in the accompanying drawings
be interpreted as illustrative and not in a limiting sense.
It is also to be understood that the following claims are to cover all
generic and specific features of the invention described herein, and all
statements of the scope of the invention which, as a matter of language,
might be said to fall therebetween.
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